Geared-neutral bidirectional positively infinitely variable rotary motion transmission

ABSTRACT

A gear-driven repositionable variable orbital disk gear driven about its user-actuated variable circular track to induce a concurrent varying second swing motion which is isolated, extracted, and cycled through the mechanism as an additional rotational product for the production of stepless infinitely variable rotational motion output is described. The gear driven disk gear drives a planetary sun gear through a telescoping shaft to transfer rotation to a geared base unit and dual output shafts through the planetary planet gears. This generates the mechanism&#39;s low speed output. User-actuated repositioning of the disk gear away from the mechanism central axis induces concurrent disk gear swing rotation as it is driven around the central axis. This swing rotation is extracted by a variable orbital arm and transferred to infinitely variably accelerate the base unit and the dual output shafts, generating the mechanism&#39;s infinitely variable output speed increases. The base unit next cycles its accelerated rotation into the rotating variable orbital arm, disk gear, and planetary sun gear through the planetary gear set planet gears to sustain the mechanism&#39;s increased operational speed. Two interconnected geared-neutral bidirectional output mechanisms are described; one integrated within the transmission, and one separated from the transmission.

TECHNICAL FIELD

This disclosure relates the transmission of angular velocity,specifically to its mechanical transmission through a continuouslyengaged gear train including a gear-driven disk gear simultaneouslyrotating and orbiting about the mechanism's central axis to produce botha first non-varying component of rotational motion and a user-actuatedsecond variable component of rotational motion which mechanicallycombine to infinitely vary the mechanism output.

BACKGROUND ART

The modern need for rotary motion transmission devices originated withthe introduction of internal combustion engines producing narrow rangesof high power output. Two forms of rotary motion transmissions appeared:(1) continuously infinitely variable traction devices, and (2) gearedmultiple-ratio shifting mechanisms. Both forms experienced seriouslimitations.

Multiple ratio gear boxes require clutching mechanisms to interruptdrive continuity during ratio shifting. Therefore the mechanisms mustincorporate ablative friction clutches or fluid torque converters whichhave limited life spans, exhaust generated energy, and are mechanicallycomplex.

Infinitely variable devices are preferable since they are capable ofbeing varied to the exact desired ratio. Therefore, efforts arecontinuing to perfect what the industry has labeled continously variabletransmission (“CVT”) designs. Continuing efforts are primarily limitedto CVT V-belts and variable roller-toroid designs. Both experiencelimitations in traction, lubrication, and premature friction-inducedfailure.

All-gear positively infinitely variable transmission devices utilizingnon-varying orbital components have been patented, all possessingserious limitations precluding their industrial adoption. These includeU.S. Pat. No. 5,308,293 (Han 1994); U.S. Pat. No. 4,854,190 (Won 1989).

Positively infinitely variable transmission devices utilizing variableorbital components have also been patented. These include U.S. Pat. No.5,352,162 (Coronel 1994) and U.S. Pat. No. 5,718,652 (Coronel 1998). The'162 patent, as with the present disclosure, utilizes a disk gear tovariably orbit the mechanism's central axis to track variable circulargear paths. The '652 patent utilizes a tilting disk gear to trackvariable circular gear paths. Both devices failed due to their inabilityto isolate, extract, and transfer as output the variable rotationalproduct. They simply exchange two inverse varying products, each ofwhich cancel the other. However, both devices taught the feasibility ofmechanically utilizing one gear to establish variable diameter geartracks capable of transferring varying angular velocity.

BRIEF DESCRIPTION OF THE DRAWINGS

The Drawing Figures

FIG. 1 shows a frontal view of the positively infinitely variabletransmission including the user-operated actuator and dual high speedand low speed output shafts.

FIG. 2 shows a top view of the core unit of the combined central coregear and two bearing races. The vertically bored slot for lateralrepositioning of the sliding driver to actuate speed changes is alsodepicted.

FIG. 3 is a top view of the orbital drive gear's track as it drivesaround the actual, non-swinging diameter of the variable orbital diskgear when the disk gear is in alignment with the mechanism central axisgenerating slow speed output. The t₁ of FIG. 3 represents an amount oftime, X, utilized to compare angular differences in orbital drive geartracking at the mechanism's slow speed operational configuration.

FIG. 4 is a top view of the orbital drive gear's track as it drivesaround the disk gear's mechanically induced smallest circular trackcreated by repositioning the orbiting disk gear away from the centralaxis, generating concurrent disk gear orbital swing during transition tothe mechanism's high speed operational configuration. The t₂ of FIG. 4represents an equal amount of time, X, utilized to demonstrateprogressively increasing angular orbital drive gear tracking during themechanism's transition to its high speed operational configuration. Theconcurrent disk gear orbital swing generated during t₂ is furtherdepicted.

FIG. 5 shows a frontal view of the geared-neutral, positively infinitelyvariable transmission's interconnected bidirectional mechanismpositioned outside the transmission.

FIG. 6 shows a frontal view of the geared-neutral, positively infinitelyvariable transmission's interconnected bidirectional mechanismpositioned within the transmission.

FIG. 7 is a top view of the transmissions's integral geared-neutralbidirectional mechanism's bored bearing and transfer shaft.

OBJECTIVES OF THE INVENTION

The objectives of the mechanism include the mechanical inception of thefollowing advantages:

1. An all-geared positively infinitely variable rotary motiontransmission.

2. A gear train utilizing one gear-driven disk gear to generate tworotational motion components: (1) gear-driven disk gear rotation, and(2) user-actuation variable disk gear swing motion which is isolated,extracted, then combined with the first motion to produce a positivelyinfinitely variable rotary motion output.

3. A positively infinitely variable transmission generating directoutput without transiting through multiple universal joints.

4. A transmission which increases the efficiency of the transfer ofpower from the motor to the vehicle wheels to increase fuel conservationand decrease pollution.

5. A positively infinitely variable transmission which is actuatedwithout injections or extractions of rotary motion.

6. A geared-neutral bidirectional positively infinitely variabletransmission eliminating the need for ablative friction clutches,hydraulic torque converters, or drive train disengagement and reversegearing.

7. A separate geared-neutral, bidirectional mechanism forinterconnection to other positively infinitely variable transmissions.

BRIEF DESCRIPTION OF THE NUMBERED PARTS WITHIN THE DRAWING FIGURES

-   1 Input Shaft-   3 Transition Actuator-   5 Control Lever-   6 Linkage Mount-   7 Transition Linkage-   8 Linkage Mount-   9 Orbital Alignment Support-   11 Input Transfer Gear-   13 Input Receiving Gear-   15 Orbital Drive Shaft-   17 Orbital Drive Gear-   19 Variable Orbital Disk Gear-   20 Disk Gear Shaft-   21 Variable Orbital Driver Arm-   22 Sliding Driver-   23 Bearing Race-   25 Bearings-   27 Bearing Race-   30 Central Core Gear-   32 Core Mount-   34 Output Receiving Gear-   36 High Speed Output Shaft-   38 Core Drive Shaft-   40 Telescoping Shaft-   42 Universal Joint-   44 Universal Joint-   46 Planetary Ring Gear-   48 Planetary Gear Mount-   50 Planet Gear-   52 Sun Gear Shaft-   54 Sun Gear-   56 Output Shaft Support-   58 Low Speed Output Shaft-   102 Input Drive Gear-   104 Input Transfer Gear-   106 Axle Shaft-   108 Constant Speed Transfer Gear-   110 Connecting Shaft-   112 Input Drive Gear-   114 Bidirectional Transfer Gear-   116 Variable Drive Gear-   117 Bidirectional Idler Shaft-   118 Bidirectional Output Gear-   120 Output Receiving Gear-   122 Bidirectional Output Shaft-   124 Variable Speed Transfer Gear-   126 Connecting Shaft-   150 Bidirectional Input Drive Gear-   155 Transfer Shaft-   156 Bored Bearing-   160 Variable Receiving Gear-   162 Bored Variable Drive Gear-   164 Variable Transfer Gear-   166 Output Receiving Gear-   168 Bidirectional Output Shaft

MODES FOR CARRYING OUT THE INVENTION Construction of the Invention

During construction of the positively infinitely variable transmissionof FIG. 1, the input shaft 1 is positioned at the mechanism's centralaxis (C/L) and journaled through supporting framework with its first endfixed to a driving motor (not shown). Centrally bored transitionactuator 3 vertically slides upon input shaft 1, is horizontally slottedaround its outer central circumference, and has linkage mount 6 attachedto its second end edge. The first end of control lever 5 slides withinthe outer circumferential slot to vertically reposition transitionactuator 3.

Orbital Alignment Support 9 is constructed with two bearing borespositioned at right angles to one another. The second end of input shaft1 is journaled through the first bearing bore of orbital alignmentsupport 9 and attached to input transfer gear 11.

Sliding orbital drive shaft 15 has a milled longitudinal keyway, and isjournaled through the second end of bearing bore of orbital alignmentsupport 9. Input receiving gear 13 is centrally bored and connected in adriven relation with input transfer gear 11, and a driving andhorizontal sliding relation with orbital drive shaft 15: utilizing a keywithin its central bore to slide within the shaft 15 keyway. Centrallybored orbital drive gear 17 is attached near one end of orbital driveshaft 15.

Variable orbital driver arm 21 has a first end extending around orbitaldrive gear 17; the end horizontally bored to journal orbital drive shaft15. Linkage mount 8 is attached to the top of the end of variableorbital arm 21. Oblong sliding driver 22 is attached to, and shares acontiguous vertical central bore with the base of the second end ofvariable orbital driver arm 21.

Disk gear shaft 20 is journaled through the contiguous central bores ofvariable orbital driver arm 21 and sliding driver 22. Variable orbitaldisk gear 19 is connected in a driven relation with orbital drive gear17, and its central bore is attached to the first end of disk gear shaft20. The second end of disk gear shaft 20 is attached to universal joint42.

Central core gear 30 is attached to bearing race 23 on its first side,and attached to bearing race 27 on its second side to form the coreunit. The core unit of parts 30, 23 & 27 rotates within framework 32upon bearings 25. Two core drive shafts 38 are attached to, and dependfrom the second side opposing ends of the core unit of parts 30, 23 &27. The core unit parts 30, 23 & 27 share a contiguous slot verticallybored through the core unit between the two core drive shafts 38.Sliding driver 22 laterally slides within this slot. The two ends of thefirst side of output shaft support 56 are attached to the second ends ofcore drive shafts 38. Low speed output shaft 58 is positioned at themechanism's central axis (C/L) and attached to the center of the secondside of output shaft support 56.

Output receiving gear 34 is connected in a driven relation with centralcore gear 30. High speed output shaft 36 is attached to the second endof output receiving gear 34.

Planetary ring gear 46 is centrally positioned around the mechanismcentral axis (C/L) and attached to supporting framework with planetarygear mount 48. Centrally bored sun gear 54 is positioned within ringgear 46 at the mechanism central axis (C/L). Sun gear shaft 52 ispositioned at the mechanism central axis (C/L), attached to universaljoint 44 on its first end, and attached to the sun gear 54 on its secondend. Telescoping shaft 40 is attached to universal joint 42 on its firstend and universal joint 44 on its second end. Two centrally bored planetgears 50 are each journaled about the second ends of core drive shafts38, and connected in a driven relation with sun gear 54, and a drivingrelation with ring gear 46.

The first end of linkage 7 is pivotally attached to linkage mount 6, andits second end is pivotally attached to linkage mount 8, wherein:movement of transition actuator 3 repositions the variable orbitaldriver arm 21 and disk gear 19 between low speed output alignment withthe mechanism central axis (C/L) at “A”, and high speed output at “B”during all operating configurations.

While FIG. 1 depicts, and this specification describes the inputreceiving gear 13 positioned to the right of the mechanism central axis(C/L), the invention may be modified with the input receiving gear 13positioned to the left of the mechanism central axis (C/L) Thismodification will permit the transmission to operate correctly withreverse direction input shaft 1 rotational input.

During construction of the transmission's interconnected bidirectionalmechanism positioned outside the transmission of FIG. 5, input drivegear 102 is attached to input shaft 1. Connecting shaft 110 is attachedto input drive gear 112 on its first end, and attached to constant speedtransfer gear 108 on its second end. Input transfer gear 104 isjournaled to rotate around axle shaft 106, and is connected to the inputdrive gear 102 in a driven relation, and to constant speed transfer gear108 in a driving relation.

Connecting shaft 126 is attached to variable drive gear 116 on its firstend, and to variable speed transfer gear 124 on its second end. Variablespeed transfer gear 124 is connected in a driven relation with thecentral core gear 30.

Two bidirectional transfer gears 114 are each journaled to rotate aroundopposite ends of bidirectional idler shaft 117, and are connected in adriven relationships with both the input drive gear 112, and variabledrive gear 116. Each end of bidirectional idler shaft 117 is journaledwithin opposing internal diameter bearings laterally b red within thebidirectional output gear 118; wherein unequal counterrotation of inputdrive gear 112 and variable drive gear 116 causes driving rotation ofthe bidirectional output gear 118 through both bidirectional transfergears 114. Output receiving gear 120 is attached to bidirectional outputshaft 122, and connected in a driven relation with the bidirectionaloutput gear 118.

During construction of the transmission's interconnected bidirectionalmechanism positioned within the transmission of FIG. 6, bidirectionalinput drive gear 150 is attached to input shaft 1. Bored variable drivegear 162 is attached to, and shares a contiguous central bore withvariable receiving gear 160 for journaled rotation around the inputshaft 1, and positioned below the bidirectional input drive gear 150.Variable transfer gear 164 is connected through a gear train (not shown)in a driven relation with the central core gear 30, and a drivingrelation with the variable receiving gear 160.

Vertically bored bearing 156 of FIG. 7 is attached to two transfershafts 155 laterally depending from opposite ends. Two bidirectionaltransfer gears 114 of FIG. 6 are each journaled to rotate around eachtransfer shaft 155. Both bidirectional transfer gears 114 are eachconnected in a driven relation with both the bidirectional input drivegear 150, and the bored variable drive gear 162. The transfer shaft 155ends are journaled within opposing internal diameter bearings laterallybored within the bidirectional output gear 118; wherein unequalcounterrotation of the bidirectional input drive gear 150 and the boredvariable drive gear 162 causes driving rotation of the bidirectionaloutput gear 118 through both bidirectional transfer gears 114. Outputreceiving gear 166 is attached to the bidirectional output shaft 168 andconnected in a driven relation with the bidirectional output gear 118.

Operation of the Invention

During operation of the positively infinitely variable transmission ofFIGS. 1 and 2, the driving motor (not shown) rotates variable orbitaldisk gear 19 through the orbital drive gear 17, orbital drive shaft 15,input receiving gear 13, input transfer gear 11, and input shaft 1.

When the variable orbital disk gear 19 rotates in alignment with themechanism central axis (C/L) at “A”, the orbital drive gear 17 tracksthe actual variable orbital disk gear 19 diameter as depicted in FIG. 3.The disk gear 19 concurrently drives the planetary sun gear 54 throughshafts 20 & 52, universal joins 42 & 44, and telescoping shaft 40.Rotation of sun gear 54 drives planet gears 50, core drive shafts 38,and the core unit (parts 30, 23 & 27) around the mechanism central axis(C/L) when operating at the mechanism's slow speed. This drives the twooutput shafts 34 and 58 at their slowest speeds, and additionallyprevents the reversal or stalling of any mechanism components atstart-up.

With user-actuated movement of control lever 5, variable orbital driverarm 21, attached sliding driver 22, and disk gear 19 are laterallyrepositioned about the core unit (parts 30, 23 & 27) away from themechanism central axis (C/L). The driving of variable orbital disk gear19 by the orbital driver gear 17 commences to track a smaller circularorbital path around the mechanism central axis (C/L) while the disk gear19 commences progressive concentric orbiting as depicted in FIG. 4.

The concurrent disk gear 19 driving of sun gear 54 orbits planet gears50, core drive shafts 38, core unit (parts 30, 23 & 27) around themechanism central axis (C/L). This compels driver arm 21 to orbitorbital drive gear 17 during its driving of disk gear 19. As orbitaldriver gear 17 continues to drive disk gear 19 around the smallercircular orbital path, a second motion not previously present is inducedby the commencement of the concentric orbiting of disk gear 19 aroundthe mechanism central axis (C/L).

This second induced motion is defined as concentric disk gear 19 swing.The t₁ of FIG. 3 depicts X amount of time that orbital drive gear 17 isdriving at the full actual diameter track of disk gear 19 at themechanism slow speed operational configuration. The t₂ of FIG. 4 alsodepicts the same X amount of time, but with orbital drive gear 17 nowdriving disk gear 19 at the mechanism's smallest diameter circulartrack, producing its full high speed operational configuration: but withthe generation of continual induced disk gear 19 swing not present at t₁when the disk gear 19 is aligned with the mechanism central axis (C/L).t₁=t₂. The amount of continual induced concentric disk gear 19 swing isproportional to the extent of disk gear 19's repositioning away from themechanism central axis (C/L). The further the center of disk gear 19 isfrom the mechanism central axis (C/L), the greater the amount ofcontinual induced swing.

This continual induced swing is isolated, extracted, and transferred asadditional rotation through enhanced swing rotation of the variableorbital arm 21, and attached sliding driver 22 to drive the core unit(parts 30, 23 & 27). Rotation of the core unit (parts 30, 23 & 27)concurrently accelerates the disk gear 19 rotation in addition to itsdriving by orbital drive gear 17. This adds the induced disk gear 19swing rotation to the orbital drive gear 17 rotation through the planetgears 50, sun gear 54, telescoping shaft 40, universal joints 42 & 44,and shafts 20 & 52. As this added motion increases the rotational speedof the disk gear 19 and variable orbital driver arm 21, it perpetuatesand continues the generation of induced swing motion, increasing thespeed of output shafts 36 and 56, until the disk gear 19 is repositionedto the mechanism central axis (C/L).

During operation of the interconnected bidirectional mechanismpositioned outside the transmission of FIG. 5, input shaft 1 rotationdrives the input drive gear 112 in a first direction through the inputtransfer gear 104, the constant speed transfer gear 108, and theconnecting shaft 110.

Variable speed transmission output from the central core gear 30 drivesthe variable drive gear 116 through the variable transfer gear 124, andconnecting shaft 126, to counterrotate the variable drive gear 116 in asecond opposite direction to the rotation of input drive gear 112.

Equal counterrotation of input drive gear 112, and variable drive gear116, equally counterrotate both bidirectional transfer gears 114 toretain bidirectional idler shaft 117, bidirectional output gear 118,output receiving gear 120, and output shaft 122 in a geared-neutral,non-rotating position.

Variable drive gear 116 rotation exceeding the rotational velocity ofinput drive gear 112, drives the bidirectional idler shaft 117,bidirectional output gear 118, output receiving gear 120, and outputshaft 122 in first directions.

Variable drive gear 116 rotation less than the rotational velocity ofinput drive gear 112 drives the bidirectional idler shaft 117,bidirectional output gear 118, output receiving gear 120, and outputshaft 122 in second opposite directions.

During operation of the interconnected bidirectional mechanismpositioned within the transmission of FIG. 6, input shaft 1 rotationdrives the attached bidirectional input drive gear 150 in a firstdirection. Variable speed transmission output from the central core gear30 (not shown) drives the bored variable drive gear 162 through theattached variable receiving gear 160, the variable transfer gear 164,and a gear train (not shown) to counterrotate the bored variable drivegear 162 in a second opposite direction to the rotation of bidirectionaldrive gear 150.

Equal counterrotation of the bidirectional input drive gear 150 and thebored variable drive gear 162, equally counterrotates both bidirectionaltransfer gears 114 to retain the bored bearing 156 & attached transfershafts 155, bidirectional output gear 118, output receiving gear 166,and output shaft 168 in a geared-neutral, non-rotating position.

Bored variable drive gear 162 rotation exceeding the rotational velocityof bidirectional input drive gear 150, drives the bored bearing 156 &attached transfer shafts 155, the bidirectional output gear 118, outputreceiving gear 166, and bidirectional output shaft 168 in firstdirections.

Bored variable drive gear 162 rotation less than the rotational velocityof bidirectional input drive gear 150 drives the bored bearing 156 &attached transfer shafts 155, the bidirectional output gear 118, outputreceiving gear 166, and output shaft 168 in second opposite directions.

INDUSTRIAL APPLICABILITY

The invention has applicability to most mechanical mechanisms whichproduce or utilize rotary motion, or would benefit from variable speedrotational motion. The prominent period urgent applications for theinvention are: the replacement of conventional multi-step manual andhydraulic shifting transmissions to permit smaller energy efficientfossil-fueled motors to operate at higher peak power speeds conservingthe fuel and operating with a more efficient angular velocity variationand transfer, eradicating conventional transmission limitations ofmechanical complexity and energy waste; the opening of new industrialand vehicular applications for variable speed changing applicationswhich are unable to utilize multi-step shifting transmissions, but couldbenefit from this device, such as aviation and marine drives, water andwind electric generating drives, endless conveyor belts, homeappliances, etc. Additional examples of existing applications for theinvention include the replacement of all conventional motorizedvehicular, machine tool, and industrial drive transmissions. Additionalexamples of new applications for the invention include conventionalelectric generation, pneumatic, and hydrostatic drive transmissions. Theinvention will replace processes not utilizing variations of input speedsuch as industrial machinery and inorganic drilling and cuttingequipment. This will permit smaller energy efficient driving motors tooperate at their maximum power generating speed with the transmissionproducing continuously engaged variation of operating, drilling orcutting speed. Fabrication of the invention is straight-forward,utilizing existing geared mechanism designing and making equipmentemployed for the production of conventional transmissions. The inventionis structurally strong capable of varying large torque loading, and iscontrollable either through direct manual actuation or existingcomputer-controlled electrical-mechanical servomotor interfaces employedin CVT mechanisms.

1. A process for utilizing a variable orbiting gear driven disk gear todrive a central core gear and high & low speed output shafts in a drivearrangement having an input shaft, an input receiving gear, a diskdriving gear, a repositionable drive gear orbital alignment shaft, arepositionable disk gear, a repositionable variable orbital driver arm,a core gear, a planetary gear set including sun and planet gears, highspeed and low speed output shafts, a central axis defined by the inputand low speed output shafts, a universally positionable connectinglinkage, the process comprising: revolving said disk driving gear andsaid repositionable variable orbital driver arm around said rotatingrepositionable disk gear through said input receiving gear, said diskdriving gear, and said repositionable drive gear orbital alignmentshaft; rotating said core gear and said high speed & low speed outputshafts through the rotating said repositionable variable orbital driverarm; translating rotation of said repositionable disk gear to drive saidplanetary gear set sun gear through said universally positionableconnecting linkage; translating said sun gear rotation to concurrentlyrotate said core gear through said planetary gear set planet gears;continuously changing the rotation speeds of said core gear, said highspeed and low speed output shafts between predetermined minimum andmaximum speeds with repositioning of said repositionable disk gearrelative to said central axis.
 2. The process as claimed in claim 1,including a process for utilizing said input shaft and said continuouslychanging rotation speeds of said core gear to drive a bidirectionaloutput gear in a drive arrangement having an input shaft drive gear, oneor more input transfer gears, an input drive gear, a variable drivegear, one or more variable speed transfer gears, one or morebidirectional transfer gears, a bidirectional idler shaft, an outputreceiving gear, and an output shaft; the process comprising: drivingsaid input drive gear in a first direction through said input shaft,said input shaft drive gear, and one or more said input transfer gears;driving said variable drive gear in a second direction through saidcontinuously changing rotational speeds of said core gear, and one ormore variable speed transfer gears; translating said input drive gearfirst direction rotation, and said variable drive gear second directionrotation to drive said bidirectional transfer gears, said bidirectionalidler shaft, said bidirectional output gear, and said output shaft at ageared-neutral non-rotating velocity when said input drive gear firstdirection speed and said variable drive gear second direction speed areequal; translating said input drive gear first direction rotation, andsaid variable drive gear second direction rotation to drive saidbidirectional transfer gears, said bidirectional idler shaft, saidbidirectional output gear, and said output shaft at infinitely variablebidirectional angular velocities when said input drive gear firstdirection speed and said variable drive gear second direction speeddiffer.
 3. The process as claimed in claim 2 with said bidirectionaloutput gear and said central axis, the process comprising: revolvingsaid bidirectional output gear around said central axis.
 4. A gear trainwith a variable orbiting gear driven disk gear driving a central coregear, and high & low speed output shafts, in a drive arrangement havingan input shaft, an input receiving gear, a disk driving gear, arepositionable drive gear orbital alignment shaft, a repositionable diskgear, a repositionable variable orbital driver arm, a core gear, aplanetary gear set including sun and planet gears, high speed and lowspeed output shafts, a central axis defined by the input and low speedoutput shafts, and a universally positionable connecting linkage,comprising: revolving means for revolving said disk driving gear andsaid repositionable variable orbital driver arm around said rotatingrepositionable disk gear through said input receiving gear, said diskdriving gear, and said repositionable drive gear orbital alignmentshaft; rotating means for rotating said core gear and said high speed &low speed output shafts through the rotating said repositionablevariable orbital driver arm; translating means for translating rotationof said repositionable disk gear to drive said planetary gear set sungear through said universally positionable connecting linkage;translating means for translating said sun gear rotation to concurrentlyrotate said core gear through said planetary gear set planet gears;continuously changing means to continuously change the rotation speedsof said core gear, said high speed and low speed output shafts betweenpredetermined minimum and maximum speeds with repositioning of saidrepositionable disk gear relative to said central axis.
 5. Thetransmission claimed in claim 4 utilizing said input shaft and saidcontinuously changing rotation speeds of said core gear to drive abidirectional output gear in a drive arrangement having an input shaftdrive gear, one or more input transfer gears, an input drive gear, avariable drive gear, one or more variable speed transfer gears, one ormore bidirectional transfer gears, a bidirectional idler shaft, anoutput receiving gear, and an output shaft; comprising: driving means todrive said input drive gear in a first direction through said inputshaft, said input shaft drive gear, and one or more said input transfergears; driving means to drive said variable drive gear in a seconddirection through said continuously changing rotational speeds of saidcore gear, and one or more variable speed transfer gears; translatingmeans to translate said input drive gear first direction rotation, andsaid variable drive gear second direction rotation to drive saidbidirectional transfer gears, said bidirectional idler shaft, saidbidirectional output gear, and said output shaft at a geared-neutralnon-rotating velocity when said input drive gear first direction speedand said variable drive gear second direction speed are equal;translating means to translate said input drive gear first directionrotation, and said variable drive gear second direction rotation todrive said bidirectional transfer gears, said bidirectional idler shaft,said bidirectional output gear, and said output shaft at infinitelyvariable bidirectional angular velocities when said input drive gearfirst direction speed and said variable drive gear second directionspeed differ.
 6. The transmission claimed in claim 5 utilizing saidbidirectional output gear and said central axis, comprising: revolvingmeans to revolve said bidirectional output gear around said centralaxis.
 7. A gear train having an infinitely variable transmissionproducing and manipulating variable orbiting gear driven disk gear, withan input shaft, a low speed output shaft, a high speed output shaft, acentral axis defined by the input shaft and the low speed output shaft,including: a driving means utilizing a orbital drive gear to drive saidvariable orbiting gear driven disk gear, and a repositionable variableorbital driver arm, around said central axis; said variable orbitinggear driven disk gear connected in a driving relation to a planetarygear set sun gear, with an universally connecting linkage means; saidrepositionable variable orbital driver arm repositionably connected in adriving relation to a core gear; said planetary gear set sun gearconnected in a driving relation with one or more planetary gear setplanet gears; wherein said variable orbiting gear driven disk gearrotation drives said core gear, said low speed output shaft, and saidhigh speed output shaft through said planetary gear set sun and planetgears; a repositioning means for repositioning said variable orbitinggear driven disk gear, and said variable orbital driver arm, in relationto said central axis; wherein repositioning of said variable orbitinggear driven disk gear and said variable orbital driver arm infinitelyvaries the rotational speeds of said core gear, said high speed and lowspeed output shafts between predetermined minimum and maximum speeds. 8.The transmission claimed in claim 7 with an interconnected bidirectionalgear train, including: interconnecting means to drive an input drivegear in a first direction through said input shaft; interconnectingmeans to drive a variable drive gear in a second direction through saidcontinuously changing rotational speeds of said core gear; translatingmeans to translate said input drive gear first direction rotation, andsaid variable drive gear second direction rotation, to drive one or morebidirectional transfer gears, a bidirectional idler shaft, abidirectional output gear, and an output shaft at a geared-neutral,non-rotating velocity, when said input drive gear first direction speed,and said variable drive gear second direction speed, are equal;translating means to translate said input drive gear first directionrotation, and said variable drive gear second direction rotation, todrive said bidirectional transfer gears, said bidirectional idler shaft,said bidirectional output gear, and said output shaft, at infinitelyvariable bidirectional angular velocities, when said input drive gearfirst direction speed, and said variable drive gear second directionspeed, differ.
 9. The transmission with an interconnected bidirectionalgear train as claimed in claim 8, including: revolving means to revolvesaid bidirectional output gear around said central axis.
 10. Thetransmission as claimed in claim 10 where the repositioning means forrepositioning the variable orbiting gear driven disk gear, and variableorbital driver arm, includes: a transition actuator linked to saidvariable orbital driver arm.
 11. The transmission as claimed in claim 10where the revolving means for revolving the disk driving gear, andrepositionable variable orbital driver arm, around the rotatingrepositionable disk gear, includes: an input transfer gear, driving aninput receiving gear repositionable laterally along an orbital driveshaft attached to an orbital drive gear.
 12. The transmission as claimedin claim 11 where the universally positionable connecting linkageincludes: a telescoping shaft attached on each end with constantvelocity universal joints.
 13. The transmission as claimed in claim 12where the interconnecting means to drive the input drive gear, and thevariable drive gear, includes: one or more gears attached to one or moregear shafts.
 14. The transmission as claimed in claim 13 where theconnecting means to connect the variably orbiting gear driven disk gearto the planetary gear set sun gear, includes: a disk gear shaft,journaled through the contiguous bore of said variable orbital driverarm and a sliding driver, attached on its first end to said variablyorbiting gear driven disk gear, and attached on its second end to a saidconstant velocity universal joint.
 15. The transmission as claimed inclaim 6 where the revolving means to revolve the bidirectional outputgear around the central axis, includes: a bidirectional transfer gearattached to, and rotating with said input shaft; a bored variable drivegear rotating around said central axis, connected with a connectingmeans to said positively infinitely variable transmission's continuouslyspeed changing output core or shaft; one or more bidirectional transfergears.
 17. A gear train to convert a positively infinitely variablerotary motion transmission to a geared-neutral bidirectionaltransmission, including: interconnecting means to drive an input drivegear in a first direction through a positively infinitely variabletransmission's constant velocity input shaft; interconnecting means todrive a variable drive gear in a second direction through the positivelyinfinitely variable transmission's continuously changing rotationalspeeds of an output shaft; translating means to translate said inputdrive gear first direction rotation, and said variable drive gear seconddirection rotation, to drive one or more bidirectional transfer gears, abidirectional idler shaft, a bidirectional output gear, and an outputshaft at a geared-neutral, non-rotating velocity, when said input drivegear first direction speed, and said variable drive gear seconddirection speed, are equal; translating means to translate said inputdrive gear first direction rotation, and said variable drive gear seconddirection rotation, to drive said bidirectional transfer gears, saidbidirectional idler shaft, said bidirectional output gear, and saidoutput shaft, at infinitely variable bidirectional angular velocities,when said input drive gear first direction speed, and said variabledrive gear second direction speed, differ.
 16. The transmission asclaimed in claim 15, including: said planetary planet gears drive saidcore gear through attached core gear shafts.